US20010018904A1 - Combustion chamber structure of in-cylinder fuel injection type engine - Google Patents
Combustion chamber structure of in-cylinder fuel injection type engine Download PDFInfo
- Publication number
- US20010018904A1 US20010018904A1 US09/799,371 US79937101A US2001018904A1 US 20010018904 A1 US20010018904 A1 US 20010018904A1 US 79937101 A US79937101 A US 79937101A US 2001018904 A1 US2001018904 A1 US 2001018904A1
- Authority
- US
- United States
- Prior art keywords
- fuel
- combustion chamber
- recess
- arrangement
- set forth
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
- F02B23/08—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition
- F02B23/10—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder
- F02B23/104—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder the injector being placed on a side position of the cylinder
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B31/00—Modifying induction systems for imparting a rotation to the charge in the cylinder
- F02B31/04—Modifying induction systems for imparting a rotation to the charge in the cylinder by means within the induction channel, e.g. deflectors
- F02B31/06—Movable means, e.g. butterfly valves
- F02B31/08—Movable means, e.g. butterfly valves having multiple air inlets, i.e. having main and auxiliary intake passages
- F02B31/085—Movable means, e.g. butterfly valves having multiple air inlets, i.e. having main and auxiliary intake passages having two inlet valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F3/00—Pistons
- F02F3/26—Pistons having combustion chamber in piston head
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
- F02B23/08—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition
- F02B23/10—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder
- F02B2023/108—Swirl flow, i.e. the axis of rotation of the main charge flow motion is vertical
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/12—Other methods of operation
- F02B2075/125—Direct injection in the combustion chamber for spark ignition engines, i.e. not in pre-combustion chamber
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F1/00—Cylinders; Cylinder heads
- F02F1/24—Cylinder heads
- F02F2001/244—Arrangement of valve stems in cylinder heads
- F02F2001/245—Arrangement of valve stems in cylinder heads the valve stems being orientated at an angle with the cylinder axis
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Definitions
- This invention relates to a four cycle internal combustion engine of the direct injected spark ignited type and more particularly to an improved combustion chamber construction for such an engine.
- direct cylinder injection is increasingly being resorted to.
- direct cylinder injection it is possible to obtain stratification of the mixture at loads less than full load. That can improve not only performance but also fuel efficiency and exhaust emission control.
- Various arrangements have been proposed to achieve this result.
- the combustion chamber is formed in part by a recess or bowl formed in the head of piston.
- the fuel is injected toward this bowl and the induction air is directed so as to cause the fuel to be swept along the surface of the bowl and redirected thereby toward the gap of the spark plug so as to insure that a stoichiometric mixture is present at the time when the spark plug is fired.
- This invention is adapted to be embodied in an internal combustion engine and more particularly to a combustion chamber therefore.
- the combustion chamber is defined by a cylinder bore, a cylinder head that closes one end of the cylinder bore and a piston that reciprocates in the cylinder bore.
- a head of the piston has a generally circular recess formed therein when viewed toward the direction of the axis of the cylinder bore.
- a fuel injector injects fuel directly into the combustion chamber.
- An arrangement is provided for causing the fuel flowing from the fuel injector to pass in a circular swirling direction around the axis of the cylinder bore and within the piston head recess .
- a spark plug is disposed on a side of the piston head recess that is diametrically opposed to the point where the fuel injector injects fuel into the combustion chamber.
- the piston head recess has a greater depth from a lower surface thereof to the facing surface of the cylinder head on one side of a diametric line extending between the fuel injector and the spark plug, then on the other side of the diametric line.
- the arrangement for effecting the flow of fuel in the circular swirling direction causes the fuel to flow first into the deeper side of the piston head recess.
- FIG. 1 is a top plan view of a piston and surrounding cylinder bore constructed in accordance with an embodiment of the invention and with certain components of the cylinder head and related induction and exhaust systems show in phantom.
- FIG. 2 is a cross sectional view taken though the upper portion of one cylinder of the engine.
- FIG. 3 is an enlarged view looking in the same general direction as FIG. 2 but taken along a different plane.
- FIG. 4 is a cross sectional view taken along the line 4 - 4 in FIG. 3.
- FIG. 5 is a top plan view, in part similar to FIG. 1, and shows another embodiment of the invention.
- a multi-cylinder internal combustion engine is identified generally by the reference numeral 11 . Since the invention deals primarily with the combustion chamber for the engine, only the upper portion of the engine is shown in the drawings and only one cylinder is depicted. It will be readily apparent to those skilled in the art how the invention can be utilized with engines having varying cylinder numbers and configurations.
- the engine 11 is comprised of a cylinder block, indicated generally by the reference numeral 12 and which defines one or more cylinder bores 13 in which pistons, indicated generally by the reference numeral 14 reciprocate.
- the cylinder bore axis is indicated as A.
- a connecting rod 15 is connected at its small end to the piston 14 via a piston pin 16 .
- the lower end of the connecting rod 15 is journalled on a throw of a crankshaft, which is not shown for the aforenoted reasons.
- the upper end of the cylinder bore 13 is closed by a cylinder head assembly that is comprised of a main cylinder head member 17 .
- This cylinder head member 17 has an recess 18 formed in its lower surface which closes the cylinder bore 13 .
- This recess 18 cooperates with the head of the piston 14 , which will be described in more detail later, to define a combustion chamber which is shown at its top dead center position in FIGS. 2 - 4 , when the clearance volume is at the minimum. It will be seen that the cylinder head recess 18 is very shallow and the piston head is domed so as to maintain as high a compression ratio as possible.
- the engine 11 is of the four valve per cylinder type although the invention is not so limited.
- a pair of intake valve seats 18 that are valved by poppet type intake valves 19 in a well known manner. These intake seats 18 lie substantially on one side of a plane containing the cylinder bore axis A and extending perpendicularly to FIG. 2.
- a pair of intake passages 21 -P and 21 -S serve the valve seats 18 .
- a suitable induction system (now shown) is affixed to one side of the cylinder head member 17 for collecting intake air.
- This induction system may be of any suitable type and can include an air inlet silencer, plenum chamber and filter mechanism.
- a throttle valve arrangement is incorporated for controlling the total air flow to the engine 11 .
- the induction system includes a main throttle valve arrangement for controlling the total air flow into the combustion chambers. The air flow direction is indicated by the arrows A.
- each cylinder of the engine is provided with an individual flow controlling valve 22 is positioned in the secondary intake passage 21 -S of each cylinder.
- This flow controlling valve controls the volume of air flow through the secondary intake passage 21 -S and is controlled by a suitable mechanism, such as a servo motor 23 or linkage system that is interconnected with the main throttle valve so as to operate in a staged sequence.
- the control strategy for opening the flow control valve 22 is such that this valve is maintained in a closed a position under idle, low speed and low mid-range running performance and opens as the low and/or speed of the engine increases. The purpose for this will described later.
- each of the intake valves 19 is urged toward its closed position by a coil compression spring 24 that operates against a surface of the cylinder head member 17 and a keeper retainer assembly which is associated with a thimble tappet 25 and which is fixed to upper ends of the stems of each of the intake valves 19 .
- exhaust passages 26 On the side of the cylinder head member 17 opposite the intake passages 21 , there are provided exhaust passages, indicated generally by the reference numeral 26 . These exhaust passages 26 are of the Siamese type and each branch thereof extends from a respective exhaust valve seat 27 that is disposed on the opposite side of the plane containing the cylinder bore axis A from the intake valve seats 18 .
- Poppet type exhaust valves 28 control the flow of exhaust gases through these exhaust valve seats 27 . These valves 28 are urged toward their closed position by coil compression springs 29 which act against machined surfaces of the cylinder head member 17 and keeper retainer assemblies that are contained within thimble tappets 31 and which are affixed to the upper ends of the stems of the exhaust valves 28 for urging them to their closed position.
- the intake valves 19 and exhaust valves 28 are operated by a valve actuating mechanism, indicated generally by the reference numeral 33 which is formed in a valve chamber 34 formed in part by the cylinder head member 17 and by a cover 35 affixed to the cylinder head member 17 .
- This valve actuating mechanism 33 includes an intake camshaft 35 which has lobes that cooperate with the intake thimble tappets 25 for opening them and their associated intake valves 19 against the action of the coil springs 24 .
- an exhaust camshaft 36 is journalled in the cylinder head assembly in a suitable manner and has cam lobes that cooperate with the exhaust thimble tappets 31 for opening the exhaust valves 28 .
- the intake and exhaust cam shafts 36 and 37 are operated so as to rotate at one half crankshaft speed in a manner well known in the art.
- this valve actuating mechanism may include a variable valve timing mechanism (WT) of any known type so as to change the valve timing and/or duration.
- WT variable valve timing mechanism
- the combustion chamber of the engine is formed at least in part by the cylinder head recess 18 and the cylinder bore 13 .
- the chamber is also formed by the head of the piston and this head is formed with a raised domed part having a generally planar upper surface 38 that lies generally along the plane that separates the intake and exhaust ports 18 and 27 and contains the cylinder bore axis A.
- An inclined downwardly extending portion 39 of this head is formed on the exhaust side and an inclined downwardly extending portion 41 is formed on the intake side.
- a bowl or recess indicated generally by the reference numeral 42 having a shape which will be defined next, is formed in the piston surfaces 38 and 41 .
- this recess has a generally circular shape when viewed in the direction of the axis A and defined by a peripheral wall 43 which is eccentrically disposed so as to lie primarily on the intake side of the combustion chamber with its innermost peripheral edge being disposed slightly upwardly of the cylinder bore axis A.
- This recess 42 has a lower wall surface 44 formed at the lower end of the wall 43 , as best seen in FIGS. 3 and 4 that slopes generally downwardly on one side of a second plane, indicated by the broken line CL 2 that contains the cylinder bore axis.
- the peripheral wall 43 has a relatively shallow curvature on the portion closer to the cylinder bore 13 than at the cylinder bore axis A.
- the lower wall surface 44 is perpendicular to a bowl axis BA (FIG. 4).
- the curved wall surface 45 is generated about the bowl axis BA.
- this curved wall portion 45 is disposed adjacent the spark gap 46 of a spark plug 47 that is mounted generally on the cylinder bore axis A.
- This spark gap 46 as best seen in FIGS. 1 and 3 and lies over the inner peripheral edge of the bowl 42 .
- a fuel injector shown only in phantom and identified generally by the reference numeral 48 is mounted in the cylinder head member 17 in a position that underlies the intake passages 21 -P and 21 -S and which has a discharge nozzle opening 49 that lies substantially on the plane CL 2 diametrically opposed to the piston bowl 42 from the spark gap 46 .
- the line CL 2 is a diametric line passing between the center of the injector nozzle opening 49 and the spark gap 46 with the injection nozzle opening 49 being positioned on the outer periphery of the bowl or recess 42 .
- the piston head portion 41 is formed with a recessed area 51 leading into the bowl 42 so as to clear the injection nozzle so that the fuel can be sprayed in a generally downward direction toward the bottom surface 44 of the bowl or recess 42 .
- an arrangement for causing the spray of fuel from the injector nozzle 49 to be directed toward the deeper side 44 A of the bowl or recess 42 first and then to swirl around the bowl side surfaces 45 toward the shallower side 44 B so as to direct the burning gases outwardly into the remainder of the combustion chamber but to maintain good stratification at the spark gap 46 at the time it is fired.
- the axis of the injector nozzle is disposed at an angle ⁇ to the centerline CL 2 as seen in FIG. 1 so as to spray toward this side of the bowl surface 41 , which surface is indicated as 44 A.
- the initial spray from injector indicated by the arrows 53 with the initial spray portion indicated at 53 A extends in a direction transversely across the recess 42 . This causes the spray to first flow into the deeper bowl portion 44 A.
- the flow control valve 22 is closed under conditions when stratification is desired, normally low and low-mid range performance so that the air flow path A will flow in a circular or swirling direction around the cylinder bore axis A.
- the fuel is turned in a direction indicated by the spray pattern 53 B to flow around the edge portion 45 of the bowl and be swept upwardly in the direction 53 C toward the spark gap 46 where it will present a stoichiometric mixture at the time the plug 47 is fired.
- the system can operate on a lean burn or stratified charge principal quite effectively.
- FIGS. 1 through 4 achieve the desired flow path in the bowl by canting both the fuel injector 48 and by providing the desired swirling motion through the use of the control valve 22 .
- FIG. 5 shows another embodiment wherein this skewed disposition of the fuel injector 48 is not required.
- the fuel injector 48 has its spray axis 51 disposed on the line CL 2 .
- the swirling motion of the intake air charge is still sufficient to provide the desired path of fuel flow as seen in this figure.
- the described embodiment provides the ability to obtain a stratified charge through the use of a bowl in the head of the piston, but the bowl configuration is such that it not only promotes the stoichiometric mixture toward the spark gap, but also promotes the flow out of the bowl into the main combustion chamber because of the slanted lower wall and also does not therefore reduce the compression ratio as with the previous type arrangement.
- the foregoing description is that of preferred embodiments of the invention and various changes and modifications may be made without departing from the spirit and scope of the invention, as defined by the appended claims.
Abstract
Description
- This invention relates to a four cycle internal combustion engine of the direct injected spark ignited type and more particularly to an improved combustion chamber construction for such an engine.
- In the interest of further improving the efficiency and performance of internal combustion engines, direct cylinder injection is increasingly being resorted to. By utilizing direct cylinder injection it is possible to obtain stratification of the mixture at loads less than full load. That can improve not only performance but also fuel efficiency and exhaust emission control. However, in attempting to inject the fuel directly into a open chamber and achieve stratification, it is necessary to insure some way in which a stoichiometric fuel/air mixture is presented at the spark gap at the time the spark plug is fired. Various arrangements have been proposed to achieve this result.
- In accordance with one type of methodology, the combustion chamber is formed in part by a recess or bowl formed in the head of piston. The fuel is injected toward this bowl and the induction air is directed so as to cause the fuel to be swept along the surface of the bowl and redirected thereby toward the gap of the spark plug so as to insure that a stoichiometric mixture is present at the time when the spark plug is fired.
- Also, in order to insure complete combustion, particularly under high speed high load conditions when a homogenous mixture is provided in the combustion chamber, it is desirable to position the spark plug close to or at the center of the combustion chamber. This means that the bowl or recess must be configured so as to direct the fuel toward the spark plug even under low speed low load conditions.
- One structure that has been proposed for this purpose is shown in published Japanese Application Hei 9-144544, published Jun. 3, 1997. This typifies the type of prior art which has been proposed to achieve this result.
- The difficulty with this prior art type of construction, however, is that in order to achieve the desired stratification under low speed low load conditions, the bowl in the piston head has had a fairly substantial volume. This means that the compression ratio of the engine is severely limited. This in turn, dictates less then optimal performance.
- It is, therefore, a principal object to this invention to provide a combustion chamber configuration wherein direct cylinder fuel injection is possible and wherein the piston head recess is made as small as possible while still achieving the desired results of stratification.
- It is a further object to this invention to provide an improved combustion chamber configuration for a direct injection engine having a high compression ratio, a central spark plug position and a bowl in the head of the piston that permits the fuel to be directed toward the gap of the spark plug without significantly adding to the clearance volume of the engine and thus maintaining a high compression ratio.
- This invention is adapted to be embodied in an internal combustion engine and more particularly to a combustion chamber therefore. The combustion chamber is defined by a cylinder bore, a cylinder head that closes one end of the cylinder bore and a piston that reciprocates in the cylinder bore. A head of the piston has a generally circular recess formed therein when viewed toward the direction of the axis of the cylinder bore. A fuel injector injects fuel directly into the combustion chamber. An arrangement is provided for causing the fuel flowing from the fuel injector to pass in a circular swirling direction around the axis of the cylinder bore and within the piston head recess . A spark plug is disposed on a side of the piston head recess that is diametrically opposed to the point where the fuel injector injects fuel into the combustion chamber. The piston head recess has a greater depth from a lower surface thereof to the facing surface of the cylinder head on one side of a diametric line extending between the fuel injector and the spark plug, then on the other side of the diametric line. The arrangement for effecting the flow of fuel in the circular swirling direction causes the fuel to flow first into the deeper side of the piston head recess.
- FIG. 1 is a top plan view of a piston and surrounding cylinder bore constructed in accordance with an embodiment of the invention and with certain components of the cylinder head and related induction and exhaust systems show in phantom.
- FIG. 2 is a cross sectional view taken though the upper portion of one cylinder of the engine.
- FIG. 3 is an enlarged view looking in the same general direction as FIG. 2 but taken along a different plane.
- FIG. 4 is a cross sectional view taken along the line4-4 in FIG. 3.
- FIG. 5 is a top plan view, in part similar to FIG. 1, and shows another embodiment of the invention.
- Referring now in detail to the drawings and first to the embodiment of FIGS.1-4, a multi-cylinder internal combustion engine is identified generally by the
reference numeral 11. Since the invention deals primarily with the combustion chamber for the engine, only the upper portion of the engine is shown in the drawings and only one cylinder is depicted. It will be readily apparent to those skilled in the art how the invention can be utilized with engines having varying cylinder numbers and configurations. - The
engine 11 is comprised of a cylinder block, indicated generally by thereference numeral 12 and which defines one ormore cylinder bores 13 in which pistons, indicated generally by thereference numeral 14 reciprocate. The cylinder bore axis is indicated as A. - A connecting
rod 15 is connected at its small end to thepiston 14 via apiston pin 16 . The lower end of the connectingrod 15 is journalled on a throw of a crankshaft, which is not shown for the aforenoted reasons. - The upper end of the
cylinder bore 13 is closed by a cylinder head assembly that is comprised of a maincylinder head member 17. Thiscylinder head member 17 has anrecess 18 formed in its lower surface which closes thecylinder bore 13. This recess 18 cooperates with the head of thepiston 14, which will be described in more detail later, to define a combustion chamber which is shown at its top dead center position in FIGS. 2-4, when the clearance volume is at the minimum. It will be seen that the cylinder head recess 18 is very shallow and the piston head is domed so as to maintain as high a compression ratio as possible. - In the illustrated embodiment, the
engine 11 is of the four valve per cylinder type although the invention is not so limited. To this end, there are provided a pair ofintake valve seats 18 that are valved by poppettype intake valves 19 in a well known manner. Theseintake seats 18 lie substantially on one side of a plane containing the cylinder bore axis A and extending perpendicularly to FIG. 2. A pair of intake passages 21-P and 21-S serve thevalve seats 18. - A suitable induction system (now shown) is affixed to one side of the
cylinder head member 17 for collecting intake air. This induction system may be of any suitable type and can include an air inlet silencer, plenum chamber and filter mechanism. In addition, a throttle valve arrangement is incorporated for controlling the total air flow to theengine 11. In addition to this, the induction system includes a main throttle valve arrangement for controlling the total air flow into the combustion chambers. The air flow direction is indicated by the arrows A. - In addition to this a main flow control throttle valve arrangement, each cylinder of the engine is provided with an individual
flow controlling valve 22 is positioned in the secondary intake passage 21-S of each cylinder. This flow controlling valve controls the volume of air flow through the secondary intake passage 21-S and is controlled by a suitable mechanism, such as aservo motor 23 or linkage system that is interconnected with the main throttle valve so as to operate in a staged sequence. The control strategy for opening theflow control valve 22 is such that this valve is maintained in a closed a position under idle, low speed and low mid-range running performance and opens as the low and/or speed of the engine increases. The purpose for this will described later. - Referring primarily to FIG. 2, each of the
intake valves 19 is urged toward its closed position by acoil compression spring 24 that operates against a surface of thecylinder head member 17 and a keeper retainer assembly which is associated with athimble tappet 25 and which is fixed to upper ends of the stems of each of theintake valves 19. - On the side of the
cylinder head member 17 opposite theintake passages 21, there are provided exhaust passages, indicated generally by thereference numeral 26. Theseexhaust passages 26 are of the Siamese type and each branch thereof extends from a respectiveexhaust valve seat 27 that is disposed on the opposite side of the plane containing the cylinder bore axis A from theintake valve seats 18. - Poppet
type exhaust valves 28 control the flow of exhaust gases through theseexhaust valve seats 27. Thesevalves 28 are urged toward their closed position bycoil compression springs 29 which act against machined surfaces of thecylinder head member 17 and keeper retainer assemblies that are contained withinthimble tappets 31 and which are affixed to the upper ends of the stems of theexhaust valves 28 for urging them to their closed position. - The exhaust gases exit the engine through a flow path defined by the
valve seats 27 and theintake passages 26 and indicated by the arrows E. These exhaust gases are collected through anexhaust manifold 32 and are discharged to the atmosphere through an associated exhaust system of a suitable type, of which is not illustrated. - The
intake valves 19 andexhaust valves 28 are operated by a valve actuating mechanism, indicated generally by thereference numeral 33 which is formed in avalve chamber 34 formed in part by thecylinder head member 17 and by acover 35 affixed to thecylinder head member 17. Thisvalve actuating mechanism 33 includes anintake camshaft 35 which has lobes that cooperate with theintake thimble tappets 25 for opening them and their associatedintake valves 19 against the action of the coil springs 24. In addition, anexhaust camshaft 36 is journalled in the cylinder head assembly in a suitable manner and has cam lobes that cooperate with theexhaust thimble tappets 31 for opening theexhaust valves 28. The intake andexhaust cam shafts - If desired, this valve actuating mechanism may include a variable valve timing mechanism (WT) of any known type so as to change the valve timing and/or duration.
- It has been noted that the combustion chamber of the engine is formed at least in part by the
cylinder head recess 18 and the cylinder bore 13. In addition, the chamber is also formed by the head of the piston and this head is formed with a raised domed part having a generally planarupper surface 38 that lies generally along the plane that separates the intake andexhaust ports portion 39 of this head is formed on the exhaust side and an inclined downwardly extendingportion 41 is formed on the intake side. Theseinclined portions upper portion 38 of the head of the piston are surrounded by a squish area. - In addition, a bowl or recess, indicated generally by the
reference numeral 42 having a shape which will be defined next, is formed in the piston surfaces 38 and 41. As best seen in FIG. 1, this recess has a generally circular shape when viewed in the direction of the axis A and defined by aperipheral wall 43 which is eccentrically disposed so as to lie primarily on the intake side of the combustion chamber with its innermost peripheral edge being disposed slightly upwardly of the cylinder bore axis A. - This
recess 42 has alower wall surface 44 formed at the lower end of thewall 43, as best seen in FIGS. 3 and 4 that slopes generally downwardly on one side of a second plane, indicated by the broken line CL2 that contains the cylinder bore axis. As may be best seen in FIG. 3, theperipheral wall 43 has a relatively shallow curvature on the portion closer to the cylinder bore 13 than at the cylinder bore axis A. In fact, there is a relatively steeply inclinedcurved wall portion 45 formed on the exhaust side of the cylinder bore 13 and piston head and also toward its central diameter. Thelower wall surface 44 is perpendicular to a bowl axis BA (FIG. 4). Thecurved wall surface 45 is generated about the bowl axis BA. - In fact, this
curved wall portion 45 is disposed adjacent thespark gap 46 of aspark plug 47 that is mounted generally on the cylinder bore axis A. Thisspark gap 46, as best seen in FIGS. 1 and 3 and lies over the inner peripheral edge of thebowl 42. - A fuel injector, shown only in phantom and identified generally by the
reference numeral 48 is mounted in thecylinder head member 17 in a position that underlies the intake passages 21-P and 21-S and which has a discharge nozzle opening 49 that lies substantially on the plane CL2 diametrically opposed to thepiston bowl 42 from thespark gap 46. Thus, the line CL2 is a diametric line passing between the center of theinjector nozzle opening 49 and thespark gap 46 with theinjection nozzle opening 49 being positioned on the outer periphery of the bowl orrecess 42. As best seen in FIG. 4, thepiston head portion 41 is formed with a recessedarea 51 leading into thebowl 42 so as to clear the injection nozzle so that the fuel can be sprayed in a generally downward direction toward thebottom surface 44 of the bowl orrecess 42. - In accordance with the invention, an arrangement is provided for causing the spray of fuel from the
injector nozzle 49 to be directed toward thedeeper side 44A of the bowl orrecess 42 first and then to swirl around the bowl side surfaces 45 toward theshallower side 44B so as to direct the burning gases outwardly into the remainder of the combustion chamber but to maintain good stratification at thespark gap 46 at the time it is fired. - In this embodiment that result is obtained in two ways. First, the axis of the injector nozzle, indicated by the
reference numeral 52, is disposed at an angle θ to the centerline CL2 as seen in FIG. 1 so as to spray toward this side of thebowl surface 41, which surface is indicated as 44A. Thus, as seen in this figure, the initial spray from injector, indicated by thearrows 53 with the initial spray portion indicated at 53A extends in a direction transversely across therecess 42. This causes the spray to first flow into thedeeper bowl portion 44A. - In addition, the
flow control valve 22 is closed under conditions when stratification is desired, normally low and low-mid range performance so that the air flow path A will flow in a circular or swirling direction around the cylinder bore axis A. Thus, the fuel is turned in a direction indicated by the spray pattern 53B to flow around theedge portion 45 of the bowl and be swept upwardly in the direction 53C toward thespark gap 46 where it will present a stoichiometric mixture at the time theplug 47 is fired. Thus, the system can operate on a lean burn or stratified charge principal quite effectively. - As noted, the embodiment of FIGS. 1 through 4 achieve the desired flow path in the bowl by canting both the
fuel injector 48 and by providing the desired swirling motion through the use of thecontrol valve 22. However, FIG. 5 shows another embodiment wherein this skewed disposition of thefuel injector 48 is not required. In this embodiment, thefuel injector 48 has itsspray axis 51 disposed on the line CL2. However, the swirling motion of the intake air charge is still sufficient to provide the desired path of fuel flow as seen in this figure. - Thus, from the foregoing description, it should be readily apparent that the described embodiment provides the ability to obtain a stratified charge through the use of a bowl in the head of the piston, but the bowl configuration is such that it not only promotes the stoichiometric mixture toward the spark gap, but also promotes the flow out of the bowl into the main combustion chamber because of the slanted lower wall and also does not therefore reduce the compression ratio as with the previous type arrangement. Of course, the foregoing description is that of preferred embodiments of the invention and various changes and modifications may be made without departing from the spirit and scope of the invention, as defined by the appended claims.
Claims (13)
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2000-061284 | 2000-03-06 | ||
JP2000061284A JP2001248447A (en) | 2000-03-06 | 2000-03-06 | Structure of combustion chamber for cylinder fuel injection engine |
JP2000-016284 | 2000-03-06 |
Publications (2)
Publication Number | Publication Date |
---|---|
US20010018904A1 true US20010018904A1 (en) | 2001-09-06 |
US6708667B2 US6708667B2 (en) | 2004-03-23 |
Family
ID=18581437
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US09/799,371 Expired - Lifetime US6708667B2 (en) | 2000-03-06 | 2001-03-05 | Combustion chamber structure of in-cylinder fuel injection type engine |
Country Status (4)
Country | Link |
---|---|
US (1) | US6708667B2 (en) |
EP (1) | EP1132591B1 (en) |
JP (1) | JP2001248447A (en) |
DE (1) | DE60111099T2 (en) |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1484498A1 (en) * | 2002-02-28 | 2004-12-08 | Yamaha Hatsudoki Kabushiki Kaisha | In-cylinder fuel injection-type internal combustion engine |
WO2012087421A1 (en) * | 2010-12-22 | 2012-06-28 | Caterpillar Inc. | Stratified charge port injection engine and method |
WO2017048511A1 (en) * | 2015-09-14 | 2017-03-23 | Westinghouse Air Brake Technologies Corporation | Compressor piston shape to reduce clearance volume |
US10036336B2 (en) | 2006-09-08 | 2018-07-31 | Hawar Technologies Limited | Apparatus to improve the efficiency of internal combustion engines, and method therefor |
US20200040807A1 (en) * | 2017-03-27 | 2020-02-06 | Mazda Motor Corporation | Spark-ignition internal combustion engine |
WO2022112035A1 (en) * | 2020-11-27 | 2022-06-02 | IFP Energies Nouvelles | Piston for an internal combustion engine, suitable for aerodynamic movement of gas |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR100471202B1 (en) * | 2001-09-26 | 2005-03-07 | 현대자동차주식회사 | Gasoline direct injection |
US7318406B2 (en) * | 2006-04-10 | 2008-01-15 | Ford Global Technologies Llc | Bowl-in-piston of a cylinder in a direct injection engine |
KR101373805B1 (en) * | 2009-11-26 | 2014-03-12 | 기아자동차주식회사 | Gasoline direct injection engine |
Family Cites Families (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5425337A (en) * | 1992-11-19 | 1995-06-20 | Izusu Ceramics Research Institute Co., Ltd. | Pre-chamber type engine |
DE69615130T2 (en) * | 1995-03-28 | 2002-06-13 | Mitsubishi Motors Corp | DIRECT INJECTION ENGINE |
JPH09144544A (en) | 1995-11-24 | 1997-06-03 | Isuzu Motors Ltd | Inside cylinder direct injection type spark ignition engine |
JP3743896B2 (en) | 1996-10-31 | 2006-02-08 | 富士重工業株式会社 | In-cylinder injection engine |
JP3746344B2 (en) * | 1996-12-24 | 2006-02-15 | トヨタ自動車株式会社 | Combustion chamber structure of internal combustion engine |
JP3030415B2 (en) | 1997-04-17 | 2000-04-10 | 三菱自動車工業株式会社 | In-cylinder injection engine piston |
JPH10317975A (en) * | 1997-05-21 | 1998-12-02 | Nissan Motor Co Ltd | Direct cylinder injection spark ignition engine |
JPH11148355A (en) * | 1997-11-14 | 1999-06-02 | Mazda Motor Corp | In-cylinder injection type spark ignition engine |
JP3644249B2 (en) * | 1998-04-22 | 2005-04-27 | 日産自動車株式会社 | In-cylinder internal combustion engine |
FR2778432B1 (en) | 1998-05-05 | 2000-06-16 | Renault | DIRECT IGNITION AND DIRECT INJECTION INTERNAL COMBUSTION ENGINE |
JP3585766B2 (en) | 1998-05-11 | 2004-11-04 | 本田技研工業株式会社 | Gasoline direct injection engine |
KR100306600B1 (en) | 1998-05-22 | 2002-03-08 | 이계안 | Piston for direct injection type gasoline engine |
-
2000
- 2000-03-06 JP JP2000061284A patent/JP2001248447A/en active Pending
-
2001
- 2001-03-05 US US09/799,371 patent/US6708667B2/en not_active Expired - Lifetime
- 2001-03-06 EP EP01105600A patent/EP1132591B1/en not_active Expired - Lifetime
- 2001-03-06 DE DE60111099T patent/DE60111099T2/en not_active Expired - Lifetime
Cited By (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20050081820A1 (en) * | 2002-02-28 | 2005-04-21 | Daijiro Tanaka | Direct injection internal combustion engine |
EP1484498A4 (en) * | 2002-02-28 | 2008-04-16 | Yamaha Motor Co Ltd | In-cylinder fuel injection-type internal combustion engine |
US7404389B2 (en) | 2002-02-28 | 2008-07-29 | Yamaha Hatsudoki Kabushiki Kaisha | Direct injection internal combustion engine |
EP1484498A1 (en) * | 2002-02-28 | 2004-12-08 | Yamaha Hatsudoki Kabushiki Kaisha | In-cylinder fuel injection-type internal combustion engine |
US10036336B2 (en) | 2006-09-08 | 2018-07-31 | Hawar Technologies Limited | Apparatus to improve the efficiency of internal combustion engines, and method therefor |
WO2012087421A1 (en) * | 2010-12-22 | 2012-06-28 | Caterpillar Inc. | Stratified charge port injection engine and method |
US8800530B2 (en) | 2010-12-22 | 2014-08-12 | Caterpillar Inc. | Stratified charge port injection engine and method |
WO2017048511A1 (en) * | 2015-09-14 | 2017-03-23 | Westinghouse Air Brake Technologies Corporation | Compressor piston shape to reduce clearance volume |
US10036381B2 (en) | 2015-09-14 | 2018-07-31 | Westinghouse Air Brake Technologies Corporation | Compressor piston shape to reduce clearance volume |
US20200040807A1 (en) * | 2017-03-27 | 2020-02-06 | Mazda Motor Corporation | Spark-ignition internal combustion engine |
US10907533B2 (en) * | 2017-03-27 | 2021-02-02 | Mazda Motor Corporation | Spark-ignition internal combustion engine |
WO2022112035A1 (en) * | 2020-11-27 | 2022-06-02 | IFP Energies Nouvelles | Piston for an internal combustion engine, suitable for aerodynamic movement of gas |
FR3116866A1 (en) * | 2020-11-27 | 2022-06-03 | IFP Energies Nouvelles | Internal combustion engine piston adapted for aerodynamic movement of gas |
Also Published As
Publication number | Publication date |
---|---|
DE60111099T2 (en) | 2005-10-27 |
DE60111099D1 (en) | 2005-07-07 |
EP1132591B1 (en) | 2005-06-01 |
EP1132591A3 (en) | 2002-03-27 |
EP1132591A2 (en) | 2001-09-12 |
JP2001248447A (en) | 2001-09-14 |
US6708667B2 (en) | 2004-03-23 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US6116211A (en) | Injection control for direct injected engine | |
US5305720A (en) | Internal combustion engine | |
US5735240A (en) | Direct injected engine | |
US5908018A (en) | Direct injected engine | |
US5724927A (en) | Direct cylinder injected engine and method of operating same | |
US5709190A (en) | Combustion chamber and induction system for engine | |
US7347181B2 (en) | Direct injection spark ignition engine | |
US6637406B2 (en) | In-cylinder injection engine with supercharger | |
US6499457B2 (en) | In-cylinder injection gasoline engine | |
US5740767A (en) | Scavenge control for engine | |
US6131554A (en) | Engine having combustion control system | |
US4532899A (en) | Internal combustion engine fuel-injection system | |
US20020046728A1 (en) | Combustion chamber for direct injection engine | |
US5799638A (en) | Direction injection system for multi-valve engine | |
US5564383A (en) | Tumble valve arrangement for engine | |
US5529038A (en) | Direct injected engine | |
US6708667B2 (en) | Combustion chamber structure of in-cylinder fuel injection type engine | |
EP0773356B1 (en) | A two-stroke cycle internal combustion engine and a method of charging same | |
US6062195A (en) | Combustion chamber for direct injected engine | |
US6269790B1 (en) | Combustion chamber for DISI engines with exhaust side piston bowl | |
US20050081820A1 (en) | Direct injection internal combustion engine | |
US5307773A (en) | Squish structure for spark ignition engine | |
US6189503B1 (en) | Porting arrangement for direct injected engine | |
US6532933B1 (en) | Fuel injection strategy for four cycle engines | |
GB2317644A (en) | Backflow of exhaust gas through exhaust valve into cylinder of i.c. engine |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: YAMAHA HATSUDOKI KABUSHIKI KAISHA, JAPAN Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:SUZUKI, YUICHI;KUROSAWA, SHINICHI;KINOSHITA, YUJI;REEL/FRAME:011610/0247 Effective date: 20010302 |
|
FEPP | Fee payment procedure |
Free format text: PAYOR NUMBER ASSIGNED (ORIGINAL EVENT CODE: ASPN); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY |
|
STCF | Information on status: patent grant |
Free format text: PATENTED CASE |
|
FPAY | Fee payment |
Year of fee payment: 4 |
|
FEPP | Fee payment procedure |
Free format text: PAYER NUMBER DE-ASSIGNED (ORIGINAL EVENT CODE: RMPN); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY Free format text: PAYOR NUMBER ASSIGNED (ORIGINAL EVENT CODE: ASPN); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY |
|
FPAY | Fee payment |
Year of fee payment: 8 |
|
FPAY | Fee payment |
Year of fee payment: 12 |